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WO2009129547A1 - Système de combustion à l’échelle mésoscopique - Google Patents

Système de combustion à l’échelle mésoscopique Download PDF

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Publication number
WO2009129547A1
WO2009129547A1 PCT/US2009/041175 US2009041175W WO2009129547A1 WO 2009129547 A1 WO2009129547 A1 WO 2009129547A1 US 2009041175 W US2009041175 W US 2009041175W WO 2009129547 A1 WO2009129547 A1 WO 2009129547A1
Authority
WO
WIPO (PCT)
Prior art keywords
meso
combustion system
scaled
fuel
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2009/041175
Other languages
English (en)
Inventor
Ajay K. Agrawal
Sadasivuni Vijaykant
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
University of Alabama UA
University of Alabama at Birmingham UAB
Original Assignee
University of Alabama UA
University of Alabama at Birmingham UAB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by University of Alabama UA, University of Alabama at Birmingham UAB filed Critical University of Alabama UA
Priority to US12/988,231 priority Critical patent/US9091434B2/en
Publication of WO2009129547A1 publication Critical patent/WO2009129547A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C99/00—Subject-matter not provided for in other groups of this subclass
    • F23C99/006—Flameless combustion stabilised within a bed of porous heat-resistant material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/12—Radiant burners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/12—Radiant burners
    • F23D14/14—Radiant burners using screens or perforated plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/03001—Miniaturized combustion devices using fluid fuels

Definitions

  • a combustion system is presented. More specifically, a meso-scaled combustion system is presented.
  • the system comprises a housing having a housing wall, a top portion defining an exhaust port, and a bottom portion having a bottom surface.
  • the housing wall defines an interior volume and at least one fuel injector port therethrough a portion of the housing wall.
  • a combustion chamber is positioned therein the interior volume of the housing.
  • the combustion chamber wall has a proximal portion adjacent the top portion of the housing and a distal portion spaced from the bottom surface of the housing.
  • there is a lid that is in sealed relation with the housing wall and the combustion chamber wall. An annulus is defined by the lid, the combustion chamber wall, and the housing wall.
  • Fig.1 is side cross-sectional view of one aspect of the combustion system
  • FIG. 2 is a side cross-sectional view of a fuel-blurring injector, according to one aspect
  • Fig. 7 illustrates measured temperature profiles at the exhaust port of the combustor of
  • Fig. 9 illustrates a temperature profile on the exterior surface of the combustor of Fig.
  • Fig. 10 illustrates the measured and computed temperature profiles of product gas temperature at exhaust port of the combustor of Fig. 1;
  • Fig. 11 illustrates measured and computed temperature profiles of product gas temperature at centerline of combustor tube of the combustor of Fig. 1.
  • Fig. 12 illustrates measured and computed temperature profile on exterior surface of the combustor of Fig. 1. DETAILED DESRIPTION OF THE INVENTION
  • the system 10 comprises a housing 100 having a housing wall 110, a top portion defining an exhaust port 130, and a bottom portion 140 having a bottom surface 145.
  • the housing wall 110 defines an interior volume 150 and at least one fuel injector port 160 therethrough a portion of the housing wall.
  • a combustion chamber 200 is positioned therein the interior volume 150 of the housing 100.
  • the combustion chamber wall 210 has a proximal portion 212 adjacent the top portion 120 of the housing and a distal portion 214 spaced from the bottom surface 145 of the housing.
  • there is a lid 300 that is in sealed relation with the housing wall and the combustion chamber wall 210.
  • FIGus 400 is defined by the lid 300, the combustion chamber wall 210, and the housing wall 110.
  • Figure 1 shows a schematic drawing of one aspect of the system showing the housing, the combustion chamber 200 concentric inside the housing 100, layers of the porous inert media 500 ("PIM"), and the lid.
  • Liquid fuel and air may be injected from one or more injection ports on the periphery of the housing.
  • the liquid fuel is kerosene.
  • the fuel is atomized, pre-vaporized, and pre-mixed with air in the annulus 400 before reaching the combustion chamber.
  • the flame may be stabilized either on the downstream surface of the top layer 506 of PIM or in the interior of the PIM.
  • the PIM comprises silicon carbide.
  • the PIM comprises a plurality of layers of PIM.
  • the first 502, second 504, and third 506 layers of PIM can be in stacked relationship with the third layer 506 having a top portion exposed to the atmosphere.
  • the first and third layers can have the same density.
  • the second layer can have a density higher than that of the first and third layers. In this aspect, the higher density of the second layer can help prevent flash back, where the flame propagates upstream of the combustion chamber 200.
  • the first and third layers have a density of 16 ccpm, and the second layer has a density of 32 ccpm.
  • all components except for the PIM may be about 1 mm thick.
  • the combustion chamber comprises an inner diameter of about 10 mm.
  • the housing comprises an inner diameter of about 15 mm.
  • the overall system is 30 mm long and 17 mm in diameter with an overall volume of 6.8 cm .
  • the volume of the combustion chamber is 2 cm , which is about an order of magnitude smaller than the previously reported liquid- fueled meso-scale combustor. Other dimensions are contemplated and are within the scope of engineering design.
  • the combustion chamber wall comprises 304-stainless steel.
  • the housing and the lid may be made a non thermally conductive material.
  • the housing 100 and the lid 300 may comprise alumino-silicate ceramic with a thermal conductivity of 1.6 W/mK. This ceramic can withstand temperatures up to 800 K, and may minimize the conduction heat transfer from combustion chamber wall to the outer surfaces, and still provided the needed structural rigidity.
  • the liquid fuel is dispersed into small droplets that can vaporize rapidly and pre-mix with air.
  • the fuel injector comprises a flow-blurring injector 600.
  • a back flow of atomizing air can be created within the fuel supply tube to form a spray with fine droplets.
  • the flow- blurring injector may comprise an inner injector tube 610, an outer injector tube 620, and an end cap 630 spaced therefrom the inner injector tube. The end cap defines an outlet port 640.
  • the air- fuel mixture exits the outlet port and is injected into the annulus.
  • Kerosene fuel was supplied by a high precision piston-cylinder fuel-pump.
  • the product gas was sampled at the exhaust port 130 using a quartz probe with a tapered tip to quench the reactions.
  • Electrochemical gas analyzers were used to measure dry product concentrations of oxygen (O 2 ) with an uncertainty of 1%, and nitric oxides (NOx) and carbon monoxide (CO) with an uncertainty of ⁇ 2 ppm.
  • the equivalence ratio was determined from the O 2 concentration in the product gas.
  • the outer surface temperature was measured by an infrared thermal imaging camera.
  • the product gas temperature was measured by an R-type thermocouple of 0.075 mm bead diameter.
  • a finite volume based computational model was developed to analyze the system performance. The conservation equations for mass, momentum, and energy were solved in an axi-symmetric domain. The model incorporated conjugate heat transfer, radiation heat transfer and heat transfer within porous media 500. Discrete ordinates model was used to simulate radiation heat transfer. The porous media was modeled as a sink term in the momentum equations. Combustion was simulated as a thin source of heat release; an assumption that is substantiated by experiments.
  • the flame can be stabilized in the interior of the PIM.
  • the reaction zone is a bright orange glow rather than a blue flame observed for a flame that was stabilized on the surface of the PIM.
  • the fuel flow rate (m f ) can be from about 3 grams/hr to about 100 grams/hr. In another aspect, the fuel flow rate can be 40 g/hr.
  • the equivalence ratio ( ⁇ ) can be from about 0.5 to about 0.8. In another aspect, the equivalence ration can be about 0.65.
  • the fuel flow rates correspond to heat release rate from about 200 W to about 5 kW.
  • Figures 3(a) and 3(b) present radial profiles of CO and NOx concentrations at the exhaust port. Both CO and NOx concentration profiles were nearly uniform in the experiment, except for slightly higher CO concentrations and lower NOx concentrations adjacent to the wall. The minor shift in CO and NOx concentrations in the wall region is attributed to the quenching effect associated with the heat loss from the combustion chamber wall. The CO concentrations are within 225 ppm and NOx concentrations are within 235 ppm. These results show excellent combustion uniformity at the combustor exit. [0034] A comparison between the surface mode and interior mode of combustion shows a slight reduction in both CO and NOx emissions when the combustor is operated in interior mode.
  • Figure 5 (a) and (b) show the effect of equivalence ratio on CO and NOx emissions.
  • Figure 7 presents the radial profile of product gas temperature at the exhaust port for
  • ⁇ 0.65.
  • the temperature profiles are parabolic in nature with peak temperature attained at the center of the combustor. The temperature at the wall region is lower because of the heat transfer from the combustion products to the reactants in the annulus. Although the peak temperatures attained at the center of the combustor are nearly the same for surface and interior modes, the temperatures near the wall region are lower for the surface combustion mode. This result indicates higher heat loss, as detailed in following sections, when the combustor is operated in surface mode of combustion compared to the interior mode. The temperature measurements in Fig. 7 are not corrected for radiation and conduction losses from the thermocouple. [0039] The axial variation in product gas temperature at the center line of the combustor tube is shown in Figure 8 for equivalence ratio of 0.65.
  • Figure 8 shows that the temperature decreases linearly along the flow direction, indicating heat transfer to the reactants in the annulus.
  • Figure 9 shows the exterior surface temperature measured by the infrared camera.
  • Results show that the exterior surface temperature is the lowest near the base.
  • the exterior surface temperature increases near the lid region, possibly because of the axial conduction through the combustor tube and further to the lid.
  • a comparison of the exterior surface temperature for the two modes of combustion reveals higher surface temperature for the surface mode of combustion. This result indicates higher heat loss from the system when the combustor is operated in the surface mode.
  • the ignition source for the system can be positioned upstream of the PIM or it can be positioned within the PIM itself. It is contemplated that conventional ignition means may be used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)

Abstract

L’invention concerne un système de combustion à l’échelle mésoscopique. Selon un aspect, le système comprend un logement doté d’une paroi de logement, une partie supérieure définissant un orifice d’évacuation, et une partie inférieure comprenant une surface inférieure. Une chambre de combustion est positionnée dans le volume intérieur du logement. La paroi de la chambre de combustion comprend une partie proximale adjacente à la partie supérieure du logement et une partie distale espacée de la surface inférieure du logement. Selon un autre aspect, l'invention comprend un couvercle en relation d’étanchéité avec la paroi de logement et la paroi de la chambre de combustion. Un espace annulaire est défini par le couvercle, la paroi de la chambre de combustion, et la paroi de logement.
PCT/US2009/041175 2008-04-18 2009-04-20 Système de combustion à l’échelle mésoscopique Ceased WO2009129547A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/988,231 US9091434B2 (en) 2008-04-18 2009-04-20 Meso-scaled combustion system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US4640308P 2008-04-18 2008-04-18
US61/046,403 2008-04-18

Publications (1)

Publication Number Publication Date
WO2009129547A1 true WO2009129547A1 (fr) 2009-10-22

Family

ID=41199495

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2009/041175 Ceased WO2009129547A1 (fr) 2008-04-18 2009-04-20 Système de combustion à l’échelle mésoscopique

Country Status (2)

Country Link
US (1) US9091434B2 (fr)
WO (1) WO2009129547A1 (fr)

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CN101975397A (zh) * 2010-09-30 2011-02-16 北京理工大学 一种液体燃料微燃烧器及其设计方法
CN104728838A (zh) * 2015-03-24 2015-06-24 华南理工大学 一种双腔液膜微型液体燃烧器及其燃烧方法

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US20140260313A1 (en) * 2013-03-12 2014-09-18 The University Of Sydney Micro-mixer/combustor
CN108348933B (zh) 2015-08-28 2022-01-28 明尼苏达州大学董事会 喷嘴和混合流体流的方法
CN105402725B (zh) * 2015-12-31 2017-09-26 重庆大学 一种用于微热光电系统的微型弥散式燃烧装置
WO2019241488A1 (fr) * 2018-06-14 2019-12-19 Regents Of The University Of Minnesota Mélangeur et atomiseur à contre-courant
US10369579B1 (en) 2018-09-04 2019-08-06 Zyxogen, Llc Multi-orifice nozzle for droplet atomization

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Publication number Priority date Publication date Assignee Title
CN101975397A (zh) * 2010-09-30 2011-02-16 北京理工大学 一种液体燃料微燃烧器及其设计方法
CN101975397B (zh) * 2010-09-30 2012-10-10 北京理工大学 一种液体燃料微燃烧器及其设计方法
CN104728838A (zh) * 2015-03-24 2015-06-24 华南理工大学 一种双腔液膜微型液体燃烧器及其燃烧方法

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